Multi-speed transmission

ABSTRACT

A multi-speed transmission with an input shaft ( 1 ) and an output shaft ( 2 ) not coaxial in relation to this, with two spur gear speeds (ST 1,  ST 2 ) that are connected tightly on the input side with the input shaft ( 1 ) rotating at an input rotational speed (n) and generate two output rotational speeds (n 1,  n 2 ), with a main gearset that is connected with the output shaft ( 2 ) and is constructed as a two webbed four shaft transmission with two coupled, shiftable planetary gearsets (RS 1,  RS 2 ) to which the output rotational speeds (n 1,  n 2 ) of the spur gear speeds (ST 1,  ST 2 ) are transferable through several shifting elements (A to E) through their selective closing to the clutch of at least six forward gears and can be shifted without group shifting. Here the output rotational speed (n 2 ) of the second ratchet speed (ST 2 ) is transferable through a first shifting element (A) to a first free shaft of the main gearset, and through a second shifting element (B) to a second shaft of the main gearset, and the rotational speed (n 1 ) of the first spur gear speed (ST 1 ), and whereby the output rotational speed (n 1 ) of the first spur gear speed (ST 1 ) is transferable through a fifth shifting element (E) to a third shaft of the main gearset. The second shaft of the main gearset is fixable through a third shifting element (C) and the third shaft of the main gearset through a fourth shifting element (D). A fourth free shaft of the main gearset is connected with the output shaft ( 2 ). In accordance with the invention, a total of six shifting elements (A to F) are provided. The output rotational speed (n 1 ) of the first spur gear speed (ST 1 ) is in addition transferable through the sixth shifting element (F) to the second shaft of the main gearset, and at least eight forward gears and maximally two reverse gears are shiftable.

[0001] The present invention concerns a multi-speed transmissionaccording to the preamble of patent Claim 1.

[0002] Several transmission schemes for automatic transmissions with anon-shiftable series assembly and a shiftable main gearset have becomeknown in U.S. Pat. No. 5,106,352 A in which a total of six forward gearsare shiftable without group shifting. The main gearset here isconstructed as a two webbed four shafted transmission with two coupledplanetary gearsets. The non-shiftable series assembly can be constructedas a single web planetary operation or as a two shafted transmissionwith two fixed spur gear pairs.

[0003] If the series assembly is constructed as a non-shiftable singleweb planetary transmission, then U.S. Pat. No. 5,106,352 A suggestsconnecting the input shaft of the automatic transmission fast with thissingle web planetary transmission and to transmit selectively the torquethus generated in the series assembly through various shift elements togearset components of the main gearset. Furthermore, the input shaft isconnectable with the main gearset through a shifting element. If theseries assembly is constructed as a two shaft transmission with constantspur gear stages, U.S. Pat. No. 5,106,352 A suggests connecting theinput shaft fast with one spur gear each of two spur gear pairs. Inputshaft and output shaft of the automatic transmission are thus notcoaxial in relation to each other. Two rotational speeds are generatedby these two spur gear pairs that are transmittable through variousshifting elements to gearset components of the main gearset.

[0004] In the older German patent application P 199 49 507.4 of theapplicant, several transmission schemas for an automatic multi-speedtransmission with various combinations of planetary gearsets aredescribed. By suitable connection of a non-shiftable planetary gearsetcombination in a series assembly to a shiftable planetary gearsetcombination in a distribution side assembly, at least seven forwardgears can be respectively shifted without group shifting. The number ofshiftable forward gears is moreover at least twice as large as thenumber of shifting elements. Series assembly and distribution sideassembly are constantly arranged coaxially in relation to each other.

[0005] DE-P 199 49 507.4 also suggests constructing the distributionside assembly as two webbed four shaft transmissions. Here anarrangement of two individual mechanically coupled single web planetarygearsets is to be understood by two webbed four shafted transmission inwhich the coupled unit has four so-called “free shafts” as a consequenceof a twofold component connection, whereby a “shaft” can be a sun gear,a hollow gear or even a web of a planetary set.

[0006] The object of the present invention now consists in that,proceeding from the state of the art mentioned, to develop a multi-speedtransmission with non-coaxial arrangement and at least seven forwardgears shiftable without group shifting with respect to building space,with low building expenditure, favorable gear gradation and greatspread.

[0007] This objective is accomplished a multi-speed transmission havingthe features of the main claim.

[0008] Proceeding from the representative state of the art of U.S. Pat.No. 5,106,352 A, the multi-speed transmission has an input shaft and anoutput shaft not arranged coaxially in relation to it. A non-shiftableseries assembly is connected with the input shaft that is constructed asa two shaft transmission with constant spur gear speeds. A shiftablemain gearset is connected with the output shaft that is constructed as atwo webbed four shaft transmission with two coupled, shiftable planetarygearsets.

[0009] The two spur gear speeds of the series assembly generate oneoutput rotational speed each of which is transferable over variousshifting elements through their selective closing on individualcomponents of the planetary gearsets of the main gearset. Obviously,various component couplings can be provided within the planetarygearsets in various refinements of the main gearset.

[0010] In accordance with the invention, the multi-speed transmissionhas six shifting elements through the selective closing of which a totalof eight forward gears and two reverse gears are shiftable. As distinctfrom the representative state of the art, an additional shifting elementis thus provided through which two additional forward gears can beshifted. Moreover, two shifting elements are shifted in each shiftedgear. In shifting from one gear into the next, only one shifting elementis shifted in this connection and a further shifting element is cut in,owing to which shifting quality-critical group shiftings in whichseveral shifting elements must be cut in and cut out at the same timeare avoided.

[0011] The first free shaft of the main gearset is connected with ashifting element through which the first shaft of the main gearset isconnectable with the second spur gear speed of the series assembly. Inaccordance with the invention, the second free shaft of the main gearsetis connected with three shifting elements through which the second shaftof the main gearset is electively connectable or fixable with the firstor the second spur gear speed of the series assembly. The third freeshaft of the main gearset is connected with two shifting elementsthrough which the third shaft of the main gearset is connectable offixable with the first spur gear speed of the series assembly. Thefourth free shaft of the main gearset is connected with the output shaftof the transmission.

[0012] Preferably, the first and second free shafts of the main gearsetare respectively a central gear, thus, a sun gear or a hollow gear. Thethird free shaft of the main gearset is preferably a web.

[0013] In relation to the representative state of the art, themulti-speed transmission of the invention thus has an additionalshifting element on the second shaft of the main gearset constructed asa two webbed four shaft transmission.

[0014] This construction makes possible compact, space-saving, eightgear multi-speed transmission for use with non-coaxial input and output.The multi-speed transmission of the invention constructed as such isespecially suited for motor vehicles with a drive motor installedcrosswise in relation to the direction of travel (“front cross drive,”“rear cross drive”), or with a drive motor installed longitudinally inrelation to the direction of travel and front or rear drive.

[0015] Preferred refinements of the invention emerge from the dependentclaims.

[0016] The invention is explained below on the basis of the designs of amulti-speed transmission represented by way of example in the figures,wherein:

[0017]FIGS. 1A and 1B represent a first design of a multi-speedtransmission of the invention;

[0018]FIGS. 2A and 2B represent a second design of a multi-speedtransmission of the invention; and

[0019]FIGS. 3A and 3B represent a third design of a multi-speedtransmission of the invention.

[0020] The transmission schema of the multi-speed transmission isrepresented in the Figures with Index A corresponding to the design inquestion. The Figure with Index B illustrates the shifting logicassociated with the design, exemplary gear ratios of the individualgears; gear gradation, transmission spread and static gear ratios.

[0021] In all Figures, an input shaft rotating with an input rotationalspeed n is designated with 1 and an output shaft of the multi-speedtransmission rotating with an output rotational speed of n is designatedwith 2. ST1 and ST2 designate a first and a second spur gear speed ofthe series assembly, in each case with an input-side spur gear S11, S21,as well as with an output-side spur gear S12, S22, respectively. On theoutput side, the series assembly thus generates two different rotationalspeeds, namely the output speed n1 with which the output side spur gearS12 of the first spur gear speed ST1 rotates and the output rotationalspeed n2 with which the output side spur gear S22 of the second spurgear speed ST2 rotates. A first and a second planetary gearset of themain gearset are designated with RS1 and RS2. The component sidecoupling of the planetary gearset components within the main gearset isdifferent in the designs represented by way of example. Six shiftingelements A, B, C, D, E, and F are provided, whereby the shiftingelements A, B, E, and F are constantly constructed as clutch and theshifting elements C, D are constantly constructed as a brake.

[0022] The first free shaft of the main gearset is connected with clutchA and rotates with closed clutch A with output rotational speed n2 ofthe second spur gear speed ST2. The second free shaft of the maingearset is connected with clutch B, brake C and clutch F, rotates whenclutch B is closed with output rotational speed n2 of the first spurgear ST2, stands still when brake C is closed, and rotates when clutch Fis closed with a rotational speed n1 of the first spur gear speed ST1.The third free shaft of the main gearset is connected with brake D andclutch E, stands still when brake D is closed and rotates with outputrotational speed n1 of the first spur gear speed ST1 when clutch E isclosed. The fourth free shaft of the main gearset is connected withoutput shaft 2 and rotates with output rotational speed nab.

[0023] In accordance with the invention, the second free shaft of themain gearset is thus, in contrast with the representative state of theart owing to the possibility of shifting the additional sixth shiftingelement F, electively connectable with both output side spur gears S12,S22 (output rotational speeds n1, n2) of the two spur gear speeds ST1,ST2, and not only with the output side spur gear S22 (output rotationalspeed n2) of the second spur gear speeds ST2.

[0024]FIG. 1A now depicts the transmission schema of an exemplary firstdesign of a multi-speed transmission of the invention. The input shaft 1(rotational speed n) is connected fast with input side spur gear S21 ofthe second spur gear speed ST2. Both planetary gearsets RS1, RS2 areconstructed as minus transmissions and enclose respectively a sun gear11, 21, a hollow gear 13, 23, as well as a web 15, 25 with planetarygears 12, 22.

[0025] The sun gear 11 of the first planetary gearset RS1 forms thefirst free shaft of the main gearset and is connectable with the outputside spur gear S22 of the second spur gear speed ST2 through the firstshifting element A. If clutch A is closed, then sun gear 11 rotates atrotational speed n2 which is calculated on the basis of the inputrotational speed n of the input shaft 1 and the gear ratio of the secondspur gear speed i_ST1.

[0026] The sun gear 21 of the second planetary gearset RS2 forms thesecond free shaft of the main gearset and is connectable with the outputside spur gear S22 of the second spur gear speed ST2 through the secondshifting element B, fixable through the third shifting element C, aswell as with the output side spur gear S12 of the first spur gear speedST1 through the sixth shifting element F. If the clutch B is closed,then sun gear 21 rotates at rotational speed n2 that is calculated onthe basis of the input rotational speed n of the input shaft 1 and thegear ratio of the second spur gear speed i_ST2. If brake C is closed,then sun gear 21 stands still. If clutch F is closed, sun gear 21rotates at rotational speed n1 that is calculated on the basis of theinput rotational speed n of the input shaft 1 and the gear ratio of thefirst spur gear speed i_ST1.

[0027] Hollow gear 13 of the first planetary gearset RS1 and the web 25of the second planetary gearset RS2 are coupled and form the third freeshaft of the main gearset. They are fixable through the fourth shiftingelement D as well as connectable through the fifth shifting element Ewith the output side spur gear S12 of the first spur gear speed ST1. Ifbrake D is closed, then hollow gear 13 and coupled web 25 stand still.If clutch E is closed, then hollow gear 13 and coupled web 25 rotate atrotational speed n1 that is calculated on the basis of the inputrotational speed n of input shaft 1 and the gear ratio of the first spurgear speed i_ST1.

[0028] Hollow gear 23 of the second planetary gearset RS2 and web 15 ofthe first planetary gearset RS1 are coupled and form the first freeshaft of the main gearset and are connected with input shaft 2 of themulti-speed transmission.

[0029] The following applies for the rotational speeds on thetransmission shafts and the shifting elements:

[0030] 1. The output rotational speed n1 of the first spur gear speedST1 is equal to the input rotational speed n of input shaft 1 divided bythe gear ratio i_ST1 of the first spur gear speed ST1;

[0031] 2. The output rotational speed n2 of the second spur gear speedST2 is equal to the input rotational speed n of input shaft 1 divided bythe gear ratio i_ST2 of the second spur gear speed ST2;

[0032] 3. The rotational speed on shifting elements A and B is equal tothe output rotational speed n2 of the second spur gear speed ST1;

[0033] 4. The rotational speed on shifting elements E and F is equal tooutput rotational speed n1 of the first spur gear speed ST2;

[0034] 5. The rotational speed on the shifted shifting element C iszero;

[0035] 6. The rotational speed on the shifted shifting element D iszero;

[0036] 7. The rotational speed on the shaft that connects shiftingelements B C, F with a central gear of the second planetary gearset RS2is negative in relation to the rotational speed present on activatedshifting element b when shifting element A and D are closed;

[0037] 8. The rotational speed on the shaft that connects shiftingelements B, C, F with the central gear of the second planetary gearsetRS2 is greater than zero when shifting element B is shifted;

[0038] 9. The rotational speed on the shaft that connects shiftingelements B, C, F with a central gear of the first planetary gearset RS1is greater than the rotational speed present when shifting element B isactivated when shifting element F is shifted;

[0039] 10. The rotational speed on the shaft that connects shiftingelement A with a central gear of the first planetary gearset RS1 isgreater than the rotational speed present on activated shifting elementA when shifting elements E and F are shifted;

[0040] 11. The rotational speed on the shaft that connects shiftingelement A with the central gear of the first planetary gearset RS1 isgreater than the rotational speed present on activated shifting elementsE and F when shifting elements E and B are shifted;

[0041] 12. The rotational speed on the shaft that connects shiftingelement A with the central gear of the first planetary gearset RS1 isgreater than the rotational speed present on activated shifting elementsE and B when shifting elements E and C are shifted;

[0042] 13. The rotational speed on the shaft that connects shiftingelement A with the central gear of the first planetary gearset RS1 isnegative in relation to the rotational speed present on activatedshifting element A when shifting elements D and B are shifted;

[0043] 14. The rotational speed on the shaft that connects shiftingelement A with the central gear of the first planetary gearset RS1 isless than the rotational speed present on activated shifting elements Dand B when shifting elements D and F are shifted;

[0044] 15. The rotational speed on the shaft that connects shiftingelement D, E with the central gear of the second planetary gearset RS2is greater than the rotational speed present on activated shiftingelements A and C when shifting elements A and B are shifted;

[0045] 16. The rotational speed on the shaft that connects shiftingelement D, E with the central gear of the second planetary gearset RS2is greater than the rotational speed present on activated shiftingelements A and B when shifting elements A and F are shifted;

[0046] 17. The rotational speed on the shaft that connects shiftingelement D, E with the central gear of the second planetary gearset RS2is greater than the rotational speed present on activated shiftingelements A and F when shifting element E is shifted.

[0047] As shown in FIG. 1B, a total of eight forward gears and tworeverse gears are shiftable in the first design of the multi-speedtransmission of the invention without comfort-critical group shiftingwith comparatively great spread and very harmonious gradation.Advantageously the starting ratio in the first forward gear and in thefirst reverse gear is great so that a torque converter can be spared asstarting element when used as a passenger car automatic transmission.The seventh and eighth forward gear is constructed drive rotationalspeed-reducing as an overdrive gear. The non-coaxial componentarrangement of input and output shaft and the compact construction ofthe multi-speed transmission are advantageous in a familiar manner for ause in motor vehicles with drive motors arranged crosswise in relationto the direction of travel.

[0048] As likewise shown in FIG. 1B, the output side spur gear S12 ofthe first spur gear speed ST1 (rotational speed n1) with (negative)rotational speed n of input shaft 1 (i_ST1=−1.0) in the first exemplarydesign of the multi-speed transmission of the invention and the outputside spur gear S22 of the second spur gear speed ST2 (rotational speedn2) with (negative) half rotational speed n of input shaft 1(i_ST2=−2.0). Other gear ratios of the two spur gear speeds ST1, ST2 canobviously be provided in other constructions of the series assembly.

[0049] Now a second exemplary design of a multi-speed transmission ofthe invention is explained on the basis of FIGS. 2A and 2B. FIG. 2Aillustrates the transmission schema of this second design. Indistinction from the previously described first design, only thecoupling of the gearset components of the main gearset and itsattachment to the individual shifting elements are modified. Shiftinglogic and exemplary static ratios and gear steps of the second designare represented in FIG. 2B that are identical to the representation inFIG. 1B corresponding to the modifications mentioned in relation to thefirst design.

[0050] As represented in FIG. 2A, the first free shaft of the maingearset constructed as a two webbed four shaft transmission continues tobe formed by a central gear of the first planetary gearset RS1,henceforth, however, by its hollow gear 13. Hollow gear 13 of the firstplanetary gearset RS1 is hence connectable with the output side spurgear S22 (rotational speed n2) of the second spur gear speed ST2 throughclutch A. The second free axle of the main gearset is henceforth formedby the two coupled sun gears 11, 21 of planetary gearsets RS1, RS2 andis connectable with the output side spur gear S22 (rotational speed n2)of the second spur gear speed ST2 through clutch B, as well as with theoutput side spur gear S12 (rotational speed n1) of the first spur gearspeed ST1 through clutch F. The third free shaft of the main gearset ishenceforth formed by the web 25 with planetary gears 22 of the secondplanetary gearset RS and is fixed unaltered through brake D as well aswith the output side spur gear S12 (rotational speed n1) of the firstspur gear speed ST1 through brake D.

[0051] In relation to the first design described, with the second designof a multi-step transmission of the invention, the main gearset is morefavorable in terms of industrial engineering owing to coupling thecomponents of the two sun gears 11, 12.

[0052]FIG. 3A represents the transmission schema of a third design of amulti-speed transmission of the invention. As distinct from thepreviously described designs one and two, the main gearset is henceforthconstructed as a Ravigneaux gearset with the known advantages regardingconstruction space.

[0053] As represented in FIG. 3A, the first planetary gearset RS1 isconstructed as a positive transmission and has two coupled webs 15′, 15″with inner planetary gears 12″ and outer planetary gears 12″. Thesecoupled webs 15′, 15″ are connected as a first clutch inside the maingearset with web 25 of planetary gears 22 of the second planetarygearset RS2, whereby the outer planetary gears 12′ of the firstplanetary gearset RS1 and the planetary gears 22 of the second planetarygearset RS2 are combined. The hollow gears 13 and 23 of both planetarygearsets RS1, RS2 are consequently likewise combined and form the secondclutch inside the main gearset.

[0054] The attachment of the free shafts of the Ravigneaux gearset tothe two spur gear speeds ST1 and ST2 corresponds to that in FIG. 1A. Theoutput rotational speed n2 of the second spur gear speed ST2 is thusconnectable with the sun gear 11 of the first planetary gearset RS1 (asa central gear of the first planetary gearset RS1) through clutch A andwith sun gear 21 of the second planetary gearset RS2 (as a central gearof the second planetary gearset RS2) through clutch B. Furthermore, theoutput rotational speed n1 of the first spur gear speed ST1 isconnectable with the coupled webs 15′, 15″, 25 of the two planetarygearsets RS1, RS2 through clutch E and in accordance with the inventionwith sun gear 21 of the second planetary gearset RS2 (as a central gearof the second planetary gearset RS2) through clutch F. Sun gear 21 isconnectable unchanged through brake C and the coupled webs 15′, 15″, 25through brake D.

[0055] Shifting logic and exemplary static gear ratios and gear steps ofthe third design are represented in FIG. 2B. Compared with thepreviously described designs one and two, the gear ratios of theindividual gears show minor deviations and the spread is somewhatlarger.

[0056] Obviously other planetary gearset combinations inside the maingearset can also be provided, in which, for example, the first or thesecond shaft of the main gearset constructed as a two webbed four shafttransmission is formed by a web of the first or second planetary gearsetRS1 or RS2.

[0057] In another construction of the multi-speed transmission of theinvention, three coupled, switchable planetary gearsets can also beprovided in the main gearset whereby it can also be appropriate(according to the coupling of these three planetary gearsets) to providea third spur gear speed that is connected on the input side fast withthe input shaft and generates a third output rotational speed that is inaddition transferable to the main gearset. In this way, compact multiplegear multi-speed transmissions with comparably small axial extent can beconstructed.

[0058] In another construction of a multi-speed transmission of theinvention, connecting the main gearset constructed as a two webbed fourshaft transmission downstream in series to a distribution side assemblycan also be provided. This distribution side assembly can benon-shiftable or shiftable through at least one additional shiftingelement, or be constructed from several coupled distribution sideassembly planetary gearsets. Reference numbers  1 Input shaft  2 Outputshaft 11 Sun gear of the first planetary gearset 12 Planetary gear ofthe first planetary gearset 13 Hollow gear of the first planetarygearset 15 Web of the first planetary gearset 21 Sun gear of the secondplanetary gearset 22 Planetary gear of the second planetary gearset 23Hollow gear of the second planetary gearset 25 Web of the secondplanetary gearset A, B, C, First to sixth shifting element D, E, F RS1First planetary gearset of the main gearset RS2 Second planetary gearsetof the main gearset ST1 First spur gear speed of the series assembly ST2Second spur gear speed of the series assembly S11 Input side spur gearof the first spur gear speed S12 Output side spur gear of the first spurgear speed S21 Input side spur gear of the second spur gear speed S22Output side spur gear of the second spur gear speed i_ST1 Gear ratio ofthe first spur gear speed i_ST2 Gear ratio of the second spur gear speedn Rotational speed of the input shaft nab Rotational speed of the outputshaft n1 Output rotational speed of the first spur gear speed n2 Outputrotational speed of the second spur gear speed

1. Multi-speed transmission with an input shaft (1) and an output shaft(2) not coaxial in relation to this, with two spur gear speeds (ST1,ST2) that are connected fast on the input side with the input shaft (1)rotating at an input rotational speed (n) and generate two outputrotational speeds (n1, n2), with a main gearset that is connected withthe output shaft (2) and is constructed as a two webbed four shafttransmission with two coupled, shiftable planetary gearsets (RS1, RS2)to which the output rotational speeds (n1, n2) of the spur gear speeds(ST1, ST2) are transferable through several shifting elements (A to E)through their selective closing to the clutch of at least six forwardgears such that, for shifting from one gear into the next higher or nextlower gear by the shifting element activated at the time, respectivelyonly one shifting element is cut out and a further shifting element iscut in, whereby the output rotational speed (n2) of the second ratchetspeed (ST2) is transferable through a first shifting element (A) to afirst free shaft of the main gearset and onto a second shifting element(B) to a second shaft of the main gearset, and whereby the outputrotational speed (n1) of the first spur gear speed (ST1) is transferablethrough a fifth shifting element (E) to a third shaft of the maingearset, whereby the second shaft of the main gearset is fixable througha third shifting element (C) and the third shaft of the main gearsetthrough a fourth shifting element (D), and whereby a fourth free shaftof the main gearset is connected with the output shaft (2), wherein atotal of six shifting elements (A to F) are provided, wherein the outputrotational speed (n1) of the first spur gear speed (ST1) is in additiontransferable through the sixth shifting element (F) to the second shaftof the main gearset, and wherein at least eight forward gears andmaximally two reverse gears are shiftable.
 2. Multi-speed transmissionaccording to claim 1, wherein the output rotational speed (n1) of thefirst spur gear speed (ST1) is, as regards amount, equal to or at leastapproximately equal to the input rotational speed (n) of the input shaft(1).
 3. Multi-speed transmission according to claim 1, wherein theoutput rotational speed (n2) of the first spur gear speed (ST2) is asregards amount equal to or at least approximately equal to the inputrotational speed (n) of the input shaft (1).
 4. Multi-speed transmissionaccording to claim 1, 2 or 3, wherein the second shaft of the maingearset is a central gear of the second planetary gearset (RS2). 5.Multi-speed transmission according to claim 1, 2 or 3, wherein thesecond shaft of the main gearset is formed of two couples central gearsof the two planetary gearsets (RS1, RS2).
 6. Multi-speed transmissionaccording to claim 1, 2 or 3, wherein the second shaft of the maingearset is built of one web (25) of the second planetary gearset (RS2)or of coupled webs (15, 25) of both planetary gearsets (RS1, RS2). 7.Multi-speed transmission according to one or more of claims 1 to 4,characterized by the following features: A sun gear (11) of the firstplanetary gearset (RS1) forms the first free shaft of the main gearsetand is connectable with an output side spur gear (S22) of the secondspur gear speed (ST2) through the first shifting element (A); A sun gear(21) of the second planetary gearset (RS2) forms the second free shaftof the main gearset and is connectable with the output side spur gear(S22) of the second spur gear speed (ST2) through the second shiftingelement (B), fixable through the third shifting element (C), as well asconnectable through the sixth shifting element (F) with an output sidespur gear (S12) of the first spur gear speed (ST1). A hollow gear (13)of the first planetary gearset (RS1) and a web (25) with planetary gears(22) of the second planetary gearset (RS2) are coupled and form thethird free shaft of he main gearset, are fixable through the fourthshifting element (D), as well as connectable with the output side spurgear (S12) of the first spur gear speed (ST1) through the fifth shiftingelement (E); and A hollow gear (23) of the second planetary gearset(RS2) and a web (15) with planetary gears (12) of the first planetarygearset (RS1) are coupled and form the fourth free shaft of the maingearset and are connected with the output shaft (2) [FIG. 1A]. 8.Multi-speed transmission according to one or more of claims 1 to 3, 5,characterized by the following features: A hollow gear (13) of the firstplanetary gearset (RS1) forms the first free shaft of the main gearsetand is connectable with an output side spur gear (S22) of the secondspur gear speed (ST2) through the first shifting element (A); A sun gear(11) of the first planetary gearset (RS1) and a sun gear (21) of thesecond planetary gearset (RS2) are coupled and form the second freeshaft of the main gearset and are connectable with the output side spurgear (S22) of the second spur gear speed element (ST2) through thesecond shifting element (B), fixable through the third shifting element(C), as well as connectable through the sixth shifting element (F) withan output side spur gear (S12) of the first spur gear speed (ST1). A web(25) with planetary gears (22) of the second planetary gearset (RS2)form the third free shaft of the main gearset, and is fixable throughthe fourth shifting element (D), as well as connectable with the outputside spur gear (S12) of the first spur gear speed (ST1) through thefifth shifting element (E); and A hollow gear (23) of the secondplanetary gearset (RS2) and a web (15) with planetary gears (12) of thefirst planetary gearset (RS1) are coupled and form the fourth free shaftof the main gearset and are connected with the output shaft (2) [FIG.2A].
 9. Multi-speed transmission according to one or more of claims 1 to4, characterized by the following features: A sun gear (11) of the firstplanetary gearset (RS1) forms the first free shaft of the main gearsetand is connectable with an output side spur gear (S22) of the secondspur gear speed (ST2) through the first shifting element (A); A sun gear(21) of the second planetary gearset (RS2) forms the second free shaftof the main gearset and is connectable with the output side spur gear(S22) of the second spur gear speed (ST2)] through the second shiftingelement (B), fixable through the third shifting element (C), as well asconnectable through the sixth shifting element (F) with an output sidespur gear (S12) of the first spur gear speed (ST1). Two coupled webs(15′, 15″) with inner and outer planetary gears (12′, 12″) of the firstplanetary gearset (RS1) and a web (25) with planetary gears (22) of thesecond planetary gearset (RS2) are coupled and form the third free shaftof the main gearset, are fixable through the fourth shifting element(D), as well as connectable with the output side spur gear (S12) of thefirst spur gear speed (ST1) through the fifth shifting element (E),whereby the outer planetary gears (12″) of the first planetary gearset(RS1) and the planetary gears (22) of the second planetary gearset (RS2)are combined; and: A hollow gear (13) of the first planetary gearset(RS1) and a hollow gear (23) of the second planetary gearset (RS2) arecombined and form the fourth free shaft of the main gearset and areconnected with the output shaft (2) [FIG. 3A].
 10. Multi-speedtransmission according to one or more of the preceding claims, wherein anon-shiftable distribution side assembly or one shiftable through atleast one additional shifting element is connected downstream in seriesfrom the main gearset with a distribution side planetary gearset orseveral coupled distribution side planetary gearsets.